WO2013049219A1 - Évaporateur de réfrigérant - Google Patents

Évaporateur de réfrigérant Download PDF

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Publication number
WO2013049219A1
WO2013049219A1 PCT/US2012/057353 US2012057353W WO2013049219A1 WO 2013049219 A1 WO2013049219 A1 WO 2013049219A1 US 2012057353 W US2012057353 W US 2012057353W WO 2013049219 A1 WO2013049219 A1 WO 2013049219A1
Authority
WO
WIPO (PCT)
Prior art keywords
tubes
refrigerant
evaporator
baffle
shell
Prior art date
Application number
PCT/US2012/057353
Other languages
English (en)
Inventor
Jon Phillip HARTFIELD
Harry Kenneth RING
Michael William GROEN
Original Assignee
Ingersoll Rand Company
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Ingersoll Rand Company filed Critical Ingersoll Rand Company
Priority to EP12836091.4A priority Critical patent/EP2769161A4/fr
Publication of WO2013049219A1 publication Critical patent/WO2013049219A1/fr
Priority to US14/226,046 priority patent/US20140202203A1/en

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F25B39/028—Evaporators having distributing means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01D—SEPARATION
    • B01D1/00—Evaporating
    • B01D1/04—Evaporators with horizontal tubes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D21/0017—Flooded core heat exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/005—Other auxiliary members within casings, e.g. internal filling means or sealing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/02—Details of evaporators
    • F25B2339/024—Evaporators with refrigerant in a vessel in which is situated a heat exchanger
    • F25B2339/0242—Evaporators with refrigerant in a vessel in which is situated a heat exchanger having tubular elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0071—Evaporators

Definitions

  • the present invention relates to heating, ventilation, and air-conditioning
  • HVAC HVAC systems
  • HVAC systems and more particularly to evaporators and evaporation methods applicable for use in HVAC and similarly associated systems.
  • flooded and falling-film evaporators are typically used in HVAC chillers to cool a process fluid (e.g., water) which, in turn, is typically used in connection with a heat exchanger coil or air-handling unit to cool air moving through the coil or air-handling unit.
  • a process fluid e.g., water
  • a heat exchanger coil or air-handling unit to cool air moving through the coil or air-handling unit.
  • a relatively large quantity of liquid refrigerant is often required to immerse a sufficient number of the tubes to achieve a high working efficiency of the evaporator.
  • excess liquid refrigerant between the tubes may contribute relatively little to the overall efficiency of the HVAC chillers, and can be an additional burden on the cost of the operating and maintaining the chillers.
  • a refrigerant evaporator including a shell having a refrigerant inlet and a refrigerant outlet, and a plurality of tubes disposed within the shell and carrying a process fluid.
  • the refrigerant evaporator also includes a baffle positioned adjacent at least some of the plurality of tubes and immersed in the liquid refrigerant to displace the liquid refrigerant.
  • FIG. 1 is a cross-sectional view of a flooded refrigerant evaporator in accordance with a first embodiment of the application, taken along line 1— 1 in FIG. 2.
  • FIG. 2 is a cross-sectional view of the flooded refrigerant evaporator of FIG. 1, taken along line 2— 2 in FIG. 1.
  • FIG. 3 is an enlarged view of a portion of the flooded refrigerant evaporator of
  • FIG. 4 is a cross-sectional view of a flooded refrigerant evaporator in accordance with a second embodiment of the application, taken along line 4— 4 in FIG. 5.
  • FIG. 5 is a cross-sectional view of the flooded refrigerant evaporator of FIG. 4, taken along line 5— 5 in FIG. 4.
  • FIG. 6 is a cross-sectional view of a falling- film refrigerant evaporator in accordance with a third embodiment of the application, taken along line 6— 6 in FIG. 7.
  • FIG. 7 is a cross-sectional view of the falling-film refrigerant evaporator of FIG.
  • FIG. 8 is an enlarged view of a portion of the falling film refrigerant evaporator of
  • FIG. 9 is a cross-sectional view of a falling-film refrigerant evaporator in accordance with a fourth embodiment of the application, taken along line 9— 9 in FIG. 10.
  • FIG. 10 is a cross-sectional view of the falling-film refrigerant evaporator of FIG.
  • FIGS. 1 and 2 illustrate a flooded refrigerant evaporator 10 used in connection with an HVAC chiller to cool a process fluid (e.g., water).
  • a process fluid e.g., water
  • a process fluid e.g., water
  • the evaporator 10 includes a shell 14 having an inlet 18 through which liquid refrigerant enters the shell 14, an outlet 22 through which gaseous refrigerant exits the shell 14, and a plurality of tubes 26 disposed within the shell 14 for carrying the process fluid.
  • the shell 14 includes a cylindrical shape (FIG.
  • the refrigerant inlet 18 and the refrigerant outlet 22 are located below and above the tubes 26, respectively, to flood the shell 14 with liquid refrigerant by introducing the liquid refrigerant below the tubes 26.
  • the tubes 26 are oriented substantially horizontally relative to a support surface of the refrigerant evaporator 10 in a series of rows (FIGS. 1 and 2) though such orientation is not a limitation of the present application or embodiment.
  • the tubes 26 depicted in the illustrated embodiment are spaced relative to each other by a triangular pitch (FIG. 1).
  • the tubes could have a rectangular pitch as shown in FIGS. 6 and 9.
  • the liquid refrigerant has a top surface 30, and a first plurality of the tubes 26 are immersed in the liquid refrigerant and located entirely below the top surface 30 of the liquid refrigerant (FIG. 1).
  • a second plurality of the tubes 26 are located at least partially above the top surface 30 of the liquid refrigerant, and are at least partially immersed in liquid refrigerant and at least partially surrounded by gaseous refrigerant.
  • a third plurality of the tubes 26 are surrounded by gaseous refrigerant and located entirely above the top surface 30 of the liquid refrigerant.
  • the refrigerant evaporator 10 also includes a baffle 34 immersed in the liquid refrigerant and positioned adjacent to the tubes 26 that are immersed in the liquid refrigerant.
  • the baffle 34 includes a plurality of apertures 38 through which the tubes 26 are received (FIG. 1 ).
  • the tubes 26 include an outer diameter less than that of the apertures 38 in which the tubes 26 are received, thereby forming an annular gap 42 between each of the tubes 26 and the baffle 34 through which liquid refrigerant may flow (FIGS. 1 and 3).
  • the baffle 34 may be positioned between adjacent tubes 26 that are immersed in the liquid refrigerant and include an outer peripheral surface containing a plurality of grooves in which the tubes are received.
  • the baffle 34 may have a smooth outer peripheral surface without any grooves and be located toward the bottom of the shell 14 below the tubes 26.
  • at least a portion of the baffle 34 is located between the lower-most tubes 26 and the shell 14 (FIGS. 1 and 2).
  • the shell 14 includes a first length L 0 and the baffle 34 includes a second length Li such that Li is about 50% of the length L 0 (FIG. 2).
  • the baffle 34 may include a length Li that is at least about 75% or about 95% of the length L 0 .
  • liquid refrigerant flows into the shell 14 via the refrigerant inlet 18.
  • the shell 14 is occupied by nearly pure liquid refrigerant because the liquid refrigerant in this region has yet to exchange heat with the tubes 26 to cause it to evaporate. Accordingly, it is considered that liquid refrigerant in this region of the shell 14 has a low void fraction.
  • the baffle 34 displaces incoming liquid refrigerant upwardly in the shell 14 toward the tubes 26 above the top surface 30 of liquid refrigerant relative to the condition if the baffle 34 were not provided.
  • the presence of the baffle 34 can act to effectively raise the top surface 30 of liquid refrigerant in the shell 14.
  • Liquid refrigerant flows through each of the annular gaps 42 and contacts the outer periphery of the tubes 26. Contact between the tubes 26 and the liquid refrigerant allows heat to be transferred from the process fluid to the liquid refrigerant. This causes the liquid refrigerant to evaporate into gaseous refrigerant (e.g. phase change), which increases the void fraction of the surrounding liquid refrigerant.
  • each of the annular gaps 42 around the periphery of the tubes 26 is locally isolated for a period of time from the rest of the refrigerant in the shell and absorbs the heat from the process fluid and evaporates into gaseous refrigerant.
  • the gaseous refrigerant bubbles through the annular gaps 42 before exiting the baffle 34 and then exits the shell 14 via the refrigerant outlet 22.
  • the void fraction within the shell 14 progressively increases from where liquid refrigerant enters the shell 14 via the refrigerant inlet 18 towards the top surface 30 of liquid refrigerant.
  • the inclusion of the baffle 34 reduces the amount of liquid refrigerant that is used compared to a typical flooded refrigerant evaporator without reducing the working efficiency of the evaporator.
  • the baffles may have a length less than the length of the Shell.
  • a plurality of baffles may be used to obtain the desired balance of refrigerant and thermal performance.
  • the baffle(s) may extend the substantial length of the shell.
  • FIGS. 4 and 5 illustrate a second construction of a flooded refrigerant evaporator
  • the evaporator 46 used in connection with an HVAC chiller to cool a process fluid. Like components are identified with like reference numerals with the letter "a,” and will not be described again in detail.
  • the evaporator 46 includes a plurality of baffles located in different positions throughout the shell 14a.
  • the flooded refrigerant evaporator 46 includes a first baffle 50 positioned adjacent the lower-most tubes 26a, a second and third baffle 54, 58 located above the first baffle 50 and axially spaced from each other, and a forth baffle 62 located above and axially spaced between the second and third baffles 54, 58.
  • the evaporator 46 may include more or fewer baffles that may be distributed throughout the shell 14a in various combinations and configurations.
  • the first, second, and third baffles 50, 54, 58 are immersed in liquid refrigerant and positioned adjacent to the tubes 26a that are immersed in the liquid refrigerant (FIG. 4).
  • the fourth baffle 62 is not entirely immersed in liquid refrigerant and is positioned adjacent to the tubes 26a that are at least partially immersed in liquid refrigerant and at least partially surrounded by gaseous refrigerant.
  • the baffles 50, 54, 58, 62 each include a plurality of apertures 38a through which the tubes 26a are received.
  • the tubes 26a include an outer diameter less than that of the apertures 38a in which the tubes 26a are received, thereby forming an annular gap 42a between each of the tubes 26a and the baffles 50, 54, 58, 62 through which liquid refrigerant may flow.
  • Each of the baffles 50, 54, 58, 62 also includes a plurality of grooves 66 in which only a portion of some of the tubes 26a is received.
  • the grooves 66 in adjacent baffles collectively define an annular gap 68 through which liquid refrigerant may flow.
  • at least a portion of the lower-most baffle 50 is located between the lower-most tubes 26a and the shell 14a (FIGS. 4 and 5).
  • the shell 14a includes a first length L 0 and the first baffle 50 includes a second length Li such that Lj is about 95% of the length L 0 (FIG. 5).
  • the second, third, and fourth baffles 54, 58, 62 include a third, fourth, and fifth length L 2 , L 3 , L 4 , respectively, such that the lengths L 2 , L 3 , and L 4 are each about 25% of the length L 0 (FIG. 5).
  • each of the baffles 54, 58, 62 may include a length that is at least about 25% to at least about 95% of the length L 0 .
  • the flooded refrigerant evaporator 46 operates in an identical fashion as the evaporator 10 shown in FIGS. 1 and 2 and described above. However, each of the baffles 50, 54, 58, 62 contributes to the displacement of the liquid refrigerant within the shell 14a an amount commensurate with the volume with the respective baffles 50, 54, 58, 62.
  • FIGS. 6 and 7 illustrate a falling-film refrigerant evaporator 70 used in connection with an HVAC chiller to cool a process fluid (e.g., water).
  • a process fluid e.g., water
  • the evaporator 70 includes a shell 74 having an inlet 78 through which liquid refrigerant enters the shell 74, an outlet 82 through which gaseous refrigerant exits the shell 74, and a plurality of tubes 86 disposed within the shell 74 for carrying a process fluid.
  • the shell 74 includes a cylindrical shape (FIG. 6).
  • the shell may include a non-cylindrical shape.
  • the refrigerant inlet 78 and outlet 82 are located above the tubes 86 to fill the shell 74 with liquid refrigerant by introducing the liquid refrigerant above the tubes 86.
  • the tubes 86 are oriented substantially horizontally relative to a support surface of the refrigerant evaporator 70 in a series of rows (FIGS. 6 and 7) though such orientation is only a non-limiting example of various possible orientations.
  • the tubes 86 in the illustrated embodiment are spaced relative to each other by a rectangular pitch (FIG. 6).
  • the tubes could have a triangular pitch as shown in FIGS. 1 and 4.
  • the liquid refrigerant has a top surface 90, and a first plurality of the tubes 86 are immersed in the liquid refrigerant and located entirely below the top surface 90 of the liquid refrigerant (FIG. 6).
  • a second plurality of the tubes 86 are located at least partially above the top surface 90 of the liquid refrigerant, and are at least partially immersed in liquid refrigerant and at least partially surrounded by gaseous refrigerant.
  • a third plurality of the tubes 86 are located entirely above the top surface 90 of the liquid refrigerant and are surrounded by gaseous refrigerant (FIG. 6).
  • the falling-film refrigerant evaporator 70 also includes a baffle 94 immersed in the liquid refrigerant and positioned adjacent to the tubes 86 that are immersed in the liquid refrigerant.
  • the baffle 94 includes a plurality of apertures 98 through which the tubes 86 are received.
  • the tubes 86 include an outer diameter less than that of the apertures 98 in which the tubes 86 are received, thereby forming an annular gap 102 between each of the tubes 86 and the baffle 94 through which liquid refrigerant may flow (FIGS. 6 and 8).
  • the baffle 94 may be positioned between adjacent tubes 86 that are immersed in the liquid refrigerant and include an outer peripheral surface containing a plurality of grooves in which the tubes 86 are received.
  • the baffle 94 may have a smooth other peripheral surface without any grooves and be located toward the bottom and sides of the shell 74 below and adjacent the tubes 86, respectively.
  • at least a portion of the baffle 94 is located between the lower-most tubes 86 and the shell 74 (FIGS. 6 and 7).
  • the shell 74 includes a first length L 0 and the baffle 94 includes a second length Li such that Lj is about 50% of the length of L 0 .
  • the baffle 94 may include a length L) that is at least about 75% or about 95% of the length L 0 .
  • liquid refrigerant falls from the refrigerant inlet 78 down through the tubes 86 generally row by row. Near the region of the bottom portion of the shell 74, the shell 74 is occupied by nearly pure liquid refrigerant because the liquid refrigerant in this region has yet to exchange heat with the tubes 86 to cause it to evaporate. Accordingly, it is considered that liquid refrigerant in this region of the shell 74 has a low void fraction.
  • the baffle 94 displaces incoming liquid refrigerant upwardly in the shell 74 toward the tubes 86 above the top surface 90 of liquid refrigerant relative to the condition if the baffle 94 were not provided.
  • the presence of the baffle 94 can act to effectively raise the top surface 90 of liquid refrigerant in the shell 74.
  • Liquid refrigerant flows through each of the annular gaps 102 and contacts the outer periphery of the tubes 86. Contact between the tubes 86 and the liquid refrigerant allows heat to be transferred from the process fluid to the liquid refrigerant.
  • the baffle 94 reduces the amount of liquid refrigerant that is used compared to a typical falling-film evaporator without reducing the working efficiency of the evaporator.
  • FIGS. 9 and 10 illustrate a second construction of a falling-film refrigerant evaporator 106 used in connection with an HVAC chiller to cool a process fluid.
  • Like components are identified with like reference numerals with the letter "a,” and will not be described again in detail.
  • the evaporator 106 includes a plurality of baffles located in different positions throughout the shell 74a.
  • the falling-film refrigerant evaporator 106 includes a first baffle 1 10 positioned adjacent the lower-most tubes 86a, a second and third baffle 1 14, 1 18 located above the first baffle 1 10 and axially spaced from each other, and a fourth baffle 122 located above and axially spaced between the second and third baffles 114, 1 18.
  • the evaporator 106 may include more or fewer baffles that may be distributed throughout the shell 74a in various combinations.
  • the first, second, and third bafflesl 10, 1 14, 1 18 are immersed in liquid refrigerant and positioned adjacent to the tubes 86a that are immersed in the liquid refrigerant (FIG.
  • the fourth baffle 122 is not entirely immersed in liquid refrigerant and is positioned adjacent to the tubes 86a that are at least partially immersed in liquid refrigerant and at least partially surrounded by gaseous refrigerant.
  • the fourth baffle 122 is also positioned adjacent to the tubes 86a that are surrounded by gaseous refrigerant.
  • the baffles 1 10, 1 14, 1 18, 122 each include a plurality of apertures 98a through which the tubes 86a are received.
  • the tubes 86a include an outer diameter less than that of the apertures 98a in which the tubes 86a are received, thereby forming an annular gap 102a between each of the tubes 86a and the baffles 1 10, 1 14, 118, 122 through which liquid refrigerant may flow.
  • at least a portion of the lower-most baffle 110 is located between the lower-most tubes 86a and the shell 74a (FIGS. 9 and 10).
  • the shell 74a includes a first length L 0 and the first baffle 110 includes a second length L] such that L] is about 95% of the length L 0 (FIG. 10).
  • the second, third, and fourth baffles 1 14, 118, 122 include a third, fourth, and fifth length L 2 , L 3 , L 4 , respectively, such that the lengths L 2 , L 3 , and L 4 are each about 25% of the length L 0 (FIG. 10).
  • each of the baffles 1 14, 1 18, 122 may include a length that is at least about 25% to at least about 95% of the length L 0 .
  • the falling-film refrigerant evaporator 106 operates in an identical fashion as the evaporator 70 shown in FIGS. 6 and 7 and described above. However, each of the baffles 1 10, 1 14, 1 18, 122 contributes to the displacement of the liquid refrigerant within the shell 74a an amount commensurate with the volume with the respective baffles 110, 1 14, 118, 122.
  • embodiments of the present application can systematically control and/or influence the rate of heat exchange by the two phased flow of refrigerant in a multidimensional environment while utilizing a static baffle, in a lower portion of the shell, for liquid refrigerant displacement.
  • the present application can be modified in one or more variants to one or more of its elements to enable an improved apparatus and method for improving the heat exchange (i.e., maximizing the reduction of heat) while optimizing the use of lesser refrigerant. It will be further appreciated that instructions of operation and/or assembly of various
  • embodiments of the present application can take the form of a kit, a retrofit assembly, or general method for operation and that such instructions may be available in a variety of formats including but not limited to print, electronic, oral, and/or visual medium.
  • embodiments of the present application may be modified in one or more variants to one or more of the characteristics of its operation (e.g., variation in process fluid temperature, vapor velocity, etc.) to enable an improved apparatus and method for improving the heat exchange (i.e., maximizing the reduction of heat) while optimizing the use of lesser refrigerant.
  • the liquid refrigerant is displaced by the physical structure of the baffle and by the refrigerant vapor generated within the gaps 42 between the outer surface of the tubes and the baffle.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

La présente invention concerne un évaporateur de réfrigérant qui comprend une enveloppe qui comporte une entrée de réfrigérant et une sortie de réfrigérant, et une pluralité de tubes qui sont disposés à l'intérieur de l'enveloppe et qui transportent un fluide de traitement. Un mode de réalisation comprend au moins une première pluralité des tubes qui sont immergés dans un réfrigérant liquide à l'intérieur de l'enveloppe, et au moins une seconde pluralité des tubes qui sont partiellement immergés dans le réfrigérant liquide et partiellement entourés par un réfrigérant gazeux. L'évaporateur de réfrigérant comprend également un déflecteur positionné de façon adjacente à la première pluralité de tubes et immergé dans le réfrigérant liquide pour déplacer le réfrigérant liquide.
PCT/US2012/057353 2011-09-26 2012-09-26 Évaporateur de réfrigérant WO2013049219A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP12836091.4A EP2769161A4 (fr) 2011-09-26 2012-09-26 Évaporateur de réfrigérant
US14/226,046 US20140202203A1 (en) 2011-09-26 2014-03-26 Refrigerant evaporator

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201161539325P 2011-09-26 2011-09-26
US61/539,325 2011-09-26

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US14/226,046 Continuation US20140202203A1 (en) 2011-09-26 2014-03-26 Refrigerant evaporator

Publications (1)

Publication Number Publication Date
WO2013049219A1 true WO2013049219A1 (fr) 2013-04-04

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US (1) US20140202203A1 (fr)
EP (1) EP2769161A4 (fr)
WO (1) WO2013049219A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104567132A (zh) * 2015-01-20 2015-04-29 珠海格力电器股份有限公司 挡液板结构以及空调设备的蒸发器
US20150247658A1 (en) * 2012-09-26 2015-09-03 Trane International Inc. Low refrigerant high performing subcooler
FR3038037A1 (fr) * 2015-06-29 2016-12-30 Trane Int Inc
EP3842724A1 (fr) * 2019-12-24 2021-06-30 Carrier Corporation Échangeur de chaleur et système d'échange de chaleur le comprenant

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20220065562A1 (en) * 2020-08-27 2022-03-03 Carrier Corporation Methods of forming protective surface treatments on heat exchagners in-situ

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3191396A (en) 1963-01-14 1965-06-29 Carrier Corp Refrigeration system and apparatus for operation at low loads
US4448348A (en) 1982-08-19 1984-05-15 Bidwell Malcolm A Forced air flue heater device
US4991648A (en) 1989-02-10 1991-02-12 Mitsubishi Jukogyo Kabushiki Kaisha Multi-tube type heat transfer apparatus
US5839294A (en) * 1996-11-19 1998-11-24 Carrier Corporation Chiller with hybrid falling film evaporator
US6952931B2 (en) 2003-10-06 2005-10-11 Asp Corporation Refrigerant monitoring system and method
US20080149311A1 (en) * 2006-12-21 2008-06-26 Industrial Technology Research Institute Spray type heat exchange device
US20080190591A1 (en) 2007-02-08 2008-08-14 Ayub Zahid H Low charge refrigerant flooded evaporator
US20110017432A1 (en) 2009-07-22 2011-01-27 Johnson Controls Technology Company Compact evaporator for chillers
US20110056664A1 (en) 2009-09-08 2011-03-10 Johnson Controls Technology Company Vapor compression system

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2805049A (en) * 1954-01-27 1957-09-03 Union Carbide Corp Heat exchanger tube spacers
US2749600A (en) * 1954-02-18 1956-06-12 Rosenblads Patenter Ab Method of making heat exchangers
US3833058A (en) * 1973-01-09 1974-09-03 Sulzer Ag Evaporator
US4593757A (en) * 1984-10-19 1986-06-10 Phillips Petroleum Company Rod baffle heat exchange apparatus and method
US5044427A (en) * 1990-08-31 1991-09-03 Phillips Petroleum Company Heat exchanger
US20090165497A1 (en) * 2007-12-31 2009-07-02 Johnson Controls Technology Company Heat exchanger
WO2009089503A2 (fr) * 2008-01-11 2009-07-16 Johnson Controls Technology Company Système de compression de vapeur

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3191396A (en) 1963-01-14 1965-06-29 Carrier Corp Refrigeration system and apparatus for operation at low loads
US4448348A (en) 1982-08-19 1984-05-15 Bidwell Malcolm A Forced air flue heater device
US4991648A (en) 1989-02-10 1991-02-12 Mitsubishi Jukogyo Kabushiki Kaisha Multi-tube type heat transfer apparatus
US5839294A (en) * 1996-11-19 1998-11-24 Carrier Corporation Chiller with hybrid falling film evaporator
US6952931B2 (en) 2003-10-06 2005-10-11 Asp Corporation Refrigerant monitoring system and method
US20080149311A1 (en) * 2006-12-21 2008-06-26 Industrial Technology Research Institute Spray type heat exchange device
US20080190591A1 (en) 2007-02-08 2008-08-14 Ayub Zahid H Low charge refrigerant flooded evaporator
US20110017432A1 (en) 2009-07-22 2011-01-27 Johnson Controls Technology Company Compact evaporator for chillers
US20110056664A1 (en) 2009-09-08 2011-03-10 Johnson Controls Technology Company Vapor compression system

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP2769161A4

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20150247658A1 (en) * 2012-09-26 2015-09-03 Trane International Inc. Low refrigerant high performing subcooler
US10627139B2 (en) 2014-11-11 2020-04-21 Trane International Inc. Suction duct and multiple suction ducts inside a shell of a flooded evaporator
US11365912B2 (en) 2014-11-11 2022-06-21 Trane International Inc. Suction duct and multiple suction ducts inside a shell of a flooded evaporator
CN104567132A (zh) * 2015-01-20 2015-04-29 珠海格力电器股份有限公司 挡液板结构以及空调设备的蒸发器
FR3038037A1 (fr) * 2015-06-29 2016-12-30 Trane Int Inc
EP3842724A1 (fr) * 2019-12-24 2021-06-30 Carrier Corporation Échangeur de chaleur et système d'échange de chaleur le comprenant
US11852425B2 (en) 2019-12-24 2023-12-26 Carrier Corporation Heat exchanger and heat exchange system including the same

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US20140202203A1 (en) 2014-07-24
EP2769161A1 (fr) 2014-08-27
EP2769161A4 (fr) 2015-08-05

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